Accessory drive mechanism



Nov. 17, 1970 L. o. HEWKO ACCESSORY DRIVE MECHANISM 2 Sheets-Sheet 1Original Filed Nov. 27. 1964 INVENTOR. ,CZ/bonyr (2 #2111623 BY gull.1477M ATTORNFY Nov. 17, 1970 L. O. HEWKO ACCESSORY DRIVE MECHANISMOriginal Filed NOV. 27- 1964 2 Sheets-Sheet 2 IN VENI'UR 10/60/711" (9Mal/37 BY I United States Patent 0 26,978 ACCESSORY DRIVE MECHANISMLubomyr 0. Hewko, Port Clinton, Ohio, assignor to General MotorsCorporation, Detroit, Mich., a corporation of Delaware Original No.3,327,566, dated June 27, 1967, Ser. No. 414,064, Nov. 27, 1964.Application for reissue June 20, 1969, Ser. No. 835,915

Int. Cl. F16c 33/38; Fl6h 13/08, 13/14 U.S. C]. 74-798 10 Claims Matterenclosed in heavy brackets appears in the original patent but forms nopart of this reissue specification; matter printed in italics indicatesthe additions made by reissue.

ABSTRACT OF THE DISCLOSURE between the oppositely disposed sphericalsurfaces, the

radius of the spherical surfaces may be the same or slightly greaterthan the radius of the ball planets; a rotatable ring in frictionalcontact with the ball planets; and an output member secured to therotatable ring.

This invention relates to an accessory drive mechanism and moreparticularly to an overdrive structure particularly adapted for drivingengine-driven accessories such as generators or alternators commonlyused on automotive vehicles.

Engine-drivcn accessories such as generators, alternators and airconditioning compressors are normally driven from the vehicle engines bymeans of belts and pulleys. In such drive arrangements the pulleydiameters may be selected to provide overdrive of engine-drivenaccessories with respect to engine speed. However, the practicaloverdrive ratio obtainable is limited due to the relationship betweenthe pulley size and belt life. It is desired to provide an overallstep-up ratio between the engine crankshaft and the alternator of 3.6to 1. This ratio exceeds the practical capabilities of pulley-beltdrives in present day automotive vehicles wherein the engines may beoperated through a Wide speed range. for example, 500 r.p.m. at idle toa maximum speed of 5000 r.p.m. With a simple belt-pulley arrangementselected to provide a 3.6 to 1 overdrive ratio, belt life is very shortand inadequate. While step-up gearing might be employed, such gear typestep-up units are not suitable due to objectionable noise at therelatively high speeds involved.

The proposed drive structure herein disclosed provides efficient, quietand vibration-free overdrive of a generator at a step-up ratio of theorder of 3.6 to l and in addition provides for improvement in normalbelt life. In order to increase belt life a portion of the desired ratiostep-up is accomplished by a planetary friction drive and a secondportion of the step-up is provided by the belt and pulleys. In thismanner, normal belt life is increased. For example, a total overdriveratio of 3.6 to l is accomplished by utilizing a 1.6 to 1 step-upplanetary traction drive and the remaining 2.25 to l stcp-up is providedby conventional all] Re. 26,978 Reissuecl Nov. 17, 1970 V-belt runningon 7.18-inch diameter and 3.18-inch diameter pulleys. With thisarrangement, at 500 r.p.m. engine idling speed, the alternator speed israised from 1150 to 1800 rpm. and its output is increased fromapproximately 9 amps to 29 amps. At 5000 engine rpm. the alternatorspeed is 18,000 r.p.m. which is within its permissible speed limit. Itwill readily be apparent that with the speeds involved that noise is avery important consideration which eliminates the use of simple step-upgearing.

The proposed friction drive structures herein disclosed are of simplestructure, are adapted for use in installations where space requirementsare critical, are inexpensive to manufacture, are capable of long usefullife, and are quiet in operation.

An object of this invention is to provide an accessory drive for drivingthe accessories of an engine-driven vehicle wherein the accessories aredriven at overdrive with respect to engine speed by means including abelt driven friction drive mechanism arranged such that one portion ofthe final overdrive ratio is obtained by belt drive and driven pulleysand a second portion by means of a friction drive transmission to assurelong normal belt life and to provide adequate overall step-up of theaccessory speed relative to engine speed to render the accessories moreeflicient particularly at relatively low engine speeds.

Another object of the invention is to provide a belt driven accessorydrive system wherein one of the belt pulleys rotates as a unit with acarrier of a friction drive transmission to drive the carrier andwherein a ball roller driven by the carrier drives a ring output memberat overdrive ratio with respect to speed of rotation of the pulley andcarrier.

A further object of this invention is to provide an accessory drivemechanism of the type described including a friction drive assemblyincluding a fixed support housing provided with an axially extendingnonrotatable support sleeve, an engine-driven input member including acarrier, bearing means supporting said input member and carrier forrotation on the external surface of the support sleeve, a rotatablering, spaced reaction suns on the external surface of the sleeve andfixed against rotation by the sleeve, a ball driven by the carrier andcontacting said suns and ring, a final power delivery shaft extendingthrough the hollow ground sleeve and a connector connecting the ring tothe final power delivery shaft extending into the fixed support sleevebetween the final power delivery shaft and the internal surface of saidsupport sleeve for driving said final power delivery shaft.

A still further object of the invention is to provide a powertransmitting mechanism wherein the carrier member includes equallyspaced axial notches for the insertion of bearing inserts having opposedspherical surfaces for receiving ball planets, the spherical surfaces ofthe inserts having a slightly larger radius than that of the balls,providing a wedged opening therebetween whereby lubricant in the wedgedopening can lift the ball planets for full hydrodynamic sphericalbearing lubrication.

An additional object of this invention is to provide an [acessory]accessory drive mechanism of the type described wherein the frictionrollcr, ring and connector cooperate to support the power delivery shaftto eliminate the need for providing a power delivery shaft bearing inaddition to the bearing for supporting the planet carrier.

These and other objects and advantages of this invention will beapparent from the following description and claims, taken in conjunctionwith the following drawings, in which:

FIG. 1 is a diagrammatic side view of a vehicle engine equipped with anaccessory and belt drive mechanism constructed in accordance with theprinciples of this invention.

FIG. 2 is an axial section through the friction roller overdrivemechanism.

FIG. 3 is a sectional view taken along the line 3-3 of FIG. 2.

FIG. 4 is a sectional view taken along the line 4-4 of FIG. 2.

FIG. 5 is a fragmentary side view of an alternate carrier constructionwhich may be substituted for the carrier of FIG. 3.

FIG. 6 is a partially sectional view illustrating the contact geometryof the basic drive between the roller and sun and roller and ring aseach being of concave profile.

FIG. 7 is a sectional view of an alternate construction wherein thefriction contact roller functions both to drive the ring and as a rollerbearing to support the power delivery shaft.

FIG. 8 is a sectional view taken along the line FIG. 7.

FIG. 9 is a sectional view of an alternate friction drive arrangementwherein two contacts are provided between the planet and sun and betweenthe planet and ring.

FIG. 10 is a partially sectional view of an arrangement similar to FIG.9 in that it provides four rolling contacts per planet and in additionillustrates the ring split into two halves with the normal load appliedby a suitable axial spring.

FIG. 11 is a partially sectional view of an arrangement wherein the ringhas two contacts and the sun at single contact with the planet.

FIG. 12 is a partially sectional view wherein there is only a singlecontact between the planet and sun and planet and ring and the geometryvery closely resembles a radial ball hearing.

In FIG. 1 there is shown an engine 10 and an alternator 14. A crankshaftdriven pulley 11 [dirves] drives an alternator pulley 12 by means of abelt 13. As heretofore stated, the pulley diameters are selected toprovide a step-up belt drive of 2.25 to 1 in order to maintain thepulley diameters within a range wherein long belt life is possible.

As best shown in FIG. 2, a ball friction roller drive indicatedgenerally at 15 provides an overdrive ratio of 1.6 to 1 between pulley12 and an alternator input shaft 40. An alternator support housing 16 isprovided with a machined surface 17 to which is attached a reactionshaft 18 provided with a machine surface 19 matching surface 17. Bolts20 maintain the shaft 18 and housing 16 in assembled relationship.Reaction shaft 18 supports the friction drive, carries the reactionforce to housing 16 and supports the belt force. Pulley 12 serves bothas the housing for the drive assembly and the carrier for the planetaryfriction drive and is the power input member for the planetary frictiondrive. A radial ball bearing 21 disposed between outer and inner races21a and 21b supports pulley 12 for rotation or reaction shaft 18. Pulley12 has formed integrally therewith a planet carrier 23 extending axiallytherefrom to receive four balls or planets 24. As best shown in FIG. 3,carrier 23 has formed therein hydrodynamic journal bearing surfaces 25for receiving balls 24. As shown in FIG. [2] 3 these surfaces 25 are[semicircular] spherical to conform to the spherical surfaces of theballs. The surfaces 25 may, however, be of other than sphericalconfiguration as hereafter set forth. Rollers 24 contact a pair ofspaced suns 26 and 27 and a ring 28. Sun 26 is fixed to reaction shaft18 so as to be incapable of rotation or axial motion and may bepressfitted upon shaft 18. Sun 27 is capable of axial motion but isincapable of rotation with respect to shaft 18. Sun 27 is grounded toreaction shaft 18 by means of a Belleville spring 29.

As best shown in FIG. 4, a pair of axially extending tangs or cars 30 onsun 27 extend into spaced slots 31 formed in Belleville spring 29.Belleville spring 29 is provided with four tangs or ears 32 which extendinto spaced radial slots 33 formed in shaft 18. In this manner,Belleville spring transmits reaction torque from sun 27 to reactionshaft 18. Referring again to FIG. 2, a spacer 34 disposed between spring29 and a snap ring 35 serves as a means for producing proper axialdeflection of spring 29 when the spring is assembled to shaft 18. Thethickness of spacer 34 is chosen to produce adequate normal load andconsequently adequate torque capacity of the drive to withstand themaximum expected torque to be transmitted. A spacer 36 disposed betweenan upstanding flange 37 on shaft 18 and race [22] 21b and a spacer 38disposed between race 21b and sun 26 insure proper axial [alignment]spacing of the parts. Ring 28, which is the power delivery member of theroller drive assembly is connected to an alternator drive shaft 40 bymeans of a drive flange 39. Drive flange 39 includes an car 41 adaptedto contact a slot 42 on ring 28 and a threaded cylindrical portion 43adapted to contact an unthreaded cylindrical sleeve spacer 44 having aradially [extended] extending flange 45 formed on the end thereof. Aball bearing 46 is disposed between alternator housing 16, and shaft 40,the race 47 supporting both the reaction shaft 18 and housing 16 and therace 48 contacting power input shaft 40. A shaft seal 49 contacts theouter surface of cylindrical sleeve spacer 44. A face seal 50 isretained against race 21a of bearing 21 adjacent spacer [38] 36 by asnap ring 51 carried by pulley 12. It will be apparent that drive flange39 is simply and easily assembled to the unit by rotating the flangerelative to shaft 40 until flange 45 contacts bearing race 48. A seal 52is disposed between a cover 53 and pulley 12. Cover 53 is retained uponpulley 12 by means of a bent-in rim 54 which extends into an annulargroove 55 in pulley 12. When assembled, lubricating oil is disposed inchamber 56 enclosed by the pulley and cover. A fan 57 supported onpulley 12 provides cooling for the alternator.

[A] As stated, suns 26 and 27 are prevented from rotation. The reactiontorque is split between suns 26 and 27 with one-half carried by eachsun. Belleville spring 29 functions both to transmit the reaction torquefrom sun 27 to reaction shaft 18 and to axially load the two suns towardeach other in order to generate normal loads at the sun-planet andring-planet contacts. The normal load when multiplied by the coefficientof traction and the radius at which it is acting, produces usable torqueforces whereby ring 28 is driven. [Semicircular] The spherical openingsor surfaces 25 are machined in the carrier 23 and constitute journalsurfaces for the ball planets 24. The halls, while rotating about theirown centerline, generate a hydrodynamic film of oil between theiroutside surfaces and the carrier surface 25 capable of supporting thetangential torque force with a minimum of wear and power losses.

As heretofore stated, the surfaces 25 of carrier 23 are [semicircular]spherical in shape and are machined on the carrier. The shape of thesesurfaces may be modified and may consist of inserts rather than beingmachined on the carrier itself. In FIG. 5, carrier 23 is shown as havingnotches 58 formed therein [and adapted to receive] having facing flat orpla'nar parallel side walls providing bearing surfaces for the flat backfaces of the bearing inserts 59. Inserts 59 are provided with sphericalsurfaces 60 which [conform more closely to] cooperate with the outerspherical surface of the ball planets 24 and produce better hydrodynamicload capacity. Here a spherical partial hydrodynamic bearing isgenerated by machining a spherical seat 60 inside the insert 59. Asindicated by the arrows, the radius of the seat is larger than theradius of the ball planet. This geometry generates a wedge actionbetween the ball planet and the seat 60. When oil is trapped in thewedge portion it tends to lift the ball slightly off the centers of thebearing inserts 59 with a relatively high force. The contact geometry ofthe basic drive is best ShOWn in FIG. 6 wherein the sun rolling surfaceand ring rolling surface are both concave. However, it is possible touse straight or convex rolling surfaces, if advantageous. The ringrolling surface illustrated as of concave profile might be of straightcylindrical shape.

In operation, pulley 12 is driven by V-belt 13 from crankshaft pulley 11of FIG. 1 and at a speed greater than crankshaft speed. In order topreserve belt life, the stepup provided by the pulleys is of the orderof 2.25 to one. Carrier 23 driven at the speed of rotation of pulley 12applies a torque force to the ball planets 24 through the partialjournal bearing surfaces 25. Suns 26, 27 being fixed to reaction shaft18 form the reaction surface for ball planets 24, causing the balls torotate about the suns. This, in turn, causes ring 28 to rotate at anincreased speed and in the same direction as pulley 12. Ring 39 drivesthe alternator input shaft 40 at a ratio of 1.6 times the speed ofrotation of pulley 12, such that the shaft 18 is driven at a speed 3.6times that of pulley 11.

In FIG. 7 there is shown a simplified roller friction drive assembly ofmore compact nature than those heretofore described. In this figure adouble pulley is welded to a cover 71, the cover 71 having bent-overtabs 72 for gripping the planet carrier 73. A reaction shaft 74 splinedto alternator housing 75 carries a roller bearing 76 having an outerrace 77 contacting carrier 73 and an inner race 78 contacting reactionshaft 74. A seal 79 prevents leakage of oil from a chamber 80 enclosedby cover 71. Race 78 contacts a shoulder 81 on shaft 74 and a spacer 82.Six ball planet rollers 83 contact spaced suns 84 and 85 and a ring 86.Sun 84 is press-fitted on reaction shaft 74 and sun 85 is connected toreaction shaft 74 by means of Belleville spring 87.

As best seen in FIG. 8, Belleville spring 87 is provided with spacednotches 88 adapted to receive ears 89 on sun 85 (shown in FIG. 7) andhas bent-over tangs 90 disposed in [semispherical] spherical seats 91formed in reaction shaft 74.

The operation is the same as that previously described, but thestructure is more compact. Belleville spring 87 is of simplifiedconstruction and the design eliminates the spacer 34 and snap ring 35 ofFIG. 2. Belleville spring 87 is simply snapped into place on shaft 74and requires no additional means of axial or torsional fastening.Another improvement consists in the elimination of the principalalternator bearing 46 of FIG. 2. In the FIG. 7 embodimentlIs] thefriction drive is further modified 80 as to function as a radial supportfor the alternator power input shaft 93. This is accomplished byproviding a pilot diameter 94 between the output flange 92 and the outerdiameter of friction drive ring 86. When flange 92 is threaded uponpower delivery shaft 93, the annular axially extending boss portion orpilot diameter 94 on flange 92 mates with the outer surface of ring 86such that the planetary rollers 8-3 support one end of shaft 93 throughsuns 84, 85 and reaction shaft 74. Deletion of the conventionalalternator bearing 46 of FIG. 2 results in considerable cost saving andstructural simplification. Belt forces are transmitted to housing 75through reaction shaft 74. In the embodiment of FIG. 7, six planet balls83 may be employed if desired. Further, in FIG. 7, a fan 95 is driven bypulley 70. Fan 95 may be disposed within housing 75 and driven by shaft93 rather than by the pulley 70. Such an arrangement is advantageous inthat the fan would then rotate at the output speed of the friction driveunit rather than its input speed.

It has heretofore been explained that the contact profiles of thecarrier may be modified to different shapes. In addition the contactarrangements may be varied as shown in FIGS. 9 through 12.

In FIG. 9 a power input carrier causes ball planets 101 to travel aroundsun 102 fixed to reaction shaft 103 to drive ring 104. In thisarrangement there are provided two contacts between the ball planet 101and sun 102 and two contacts between ball planet 101 and ring 104. Thisarrangement increases the axial stiffness of the drive. The requirednormal load between the rolling bodies is generated by interference fitbetween the three rolling bodies.

6 The flexibility of the various members is effectively utilized as aloading spring.

FIG. 10 shows an additional arrangement having four rolling contacts perplanet. Herein the ring 109 is divided into two halves 107 and 108 withthe ring portion 107 keyed to portion [109] 108 for axial movement withrespect thereto. A Belleville spring 110 seated upon a snap ring 111provides proper normal loading of the rolling members. Sun 106 isprevented from rotation by a reaction shaft 112. Carrier 105 is theinput and ring 109 the power delivery member. This design does notdepend upon dimensional interference fit for loading, but uses theseparate, preferably flat rate spring 110.

FIG. 11 shows a further contact arrangement wherein the ball planet 113has two contacts with ring 114 and a single contact with sun 115. Thenormal loading of the rolling bodies is again accomplished byinterference fit using the elasticity of the rolling elements as aspring. Sun 115 is held against rotation by a reaction shaft 116,carrier [112] 112 is input, and ring 114 the output of the assembly.

In FIG. 12 there is only one contact between the ball planet 121 and sun118 and one contact between the ball 121 and ring 120. The geometryclosely resembles a radial ball bearing. Here, again, the normal load inthe contact is generated by dimensional interference of the rollingmembers. Sun 118 is held against rotation by reaction shaft 119, carrier117 is the input, and ring 120 the output of the unit.

It will readily be understood that the carriers of FIGS. 9 through 12will be belt-driven and the rings connected to an alternator input shaft(not shown) as described in FIGS. 2 and 7.

Depending upon applications, each of the suggested arrangements has itsown advantages. The fixed preload or interference preload arrangementsare best suited for drive applications where the drive is required tooperate at predominantly constant load. The spring preload arrangementhaving split sun or split ring is best suited where dimensional accuracycannot be maintained, thus providing the required contact normal loadswith relatively liberal manufacturing tolerance.

There has thus been provided a simple compact and inexpensive overdriveassembly particularly designed for driving an alternator of the typecommonly used in automotive vehicles. The axial load required totransmit the peak torque of 36 inch pounds is relatively low. resultingin small loss of etficiency and long useful life. The drive provides anormal step-up of alternator speed which is quiet and vibration-free atall speeds due to the uninterrupted action of the rolling contacts andthe continuous balance of all radial and axial force vectors betweenrolling bodies. In addition to displaying an absence of exciting forces,the traction drives behave dynamically as a staff viscous damper. Thischaracteristic is of great benefit in applications containingobjectionable natural vibration frequencies within their operating speedrange, since the need for vibration dampeners is eliminated. Theapplication is ideal for engine-driven alternators where quiet operationis essential and belt life is preserved by reducing the step-up providedby the belt and by supplying a portion of the step-up through thefriction drive assembly.

What is claimed is:

1. Power transmitting mechanism comprising a nonrotatable housing, ahollow sleeve shaft fixed to said housing, a power input carrier, abearing supporting said carrier on said sleeve shaft for rotation withrespect to said shaft, a first sun carried by said shaft and fixedagainst movement with respect to said shaft, a second sun carried bysaid shaft and axially movable with respect thereto, means connectingsaid second sun to said sleeve shaft comprising a Belleville washer,said washer preventing rotation of said second sun and effective to biassaid second sun axially toward said first sun, a ring spaced from saidsuns, said carrier extending into the space hetween said suns and ring,spaced surfaces on said carrier for receiving ball rollers, a torquetransmitting ball disposed in the space between each of said spacedsurfaces of said carrier and in nonslipping friction engagement withsaid ring and suns, a power delivery shaft extending through said hollowsleeve shaft, a bearing between said housing and power delivery shaft,and means connecting said ring to said power delivery shaft. said torquetransmitting balls also providing a bearing support for said powerdelivery shaft] 2. Power transmitting mechanism comprising a housingfixed against rotation, a hollow sleeve support shaft extendingoutwardly from said housing and fixed thereto, a power input planetcarrier, a bearing rotatably supporting said carrier on said sleeveshaft, a first sun supported upon said sleeve shaft in fixedrelationship with respect thereto, a second sun supported on said sleeveshaft and movable with respect thereto, a ring spaced from said suns, anextension on said carrier extending into the space between said ring andsuns, a plurality of ball receiving pockets on said extension, a ball ineach of said pockets, means for biasing said second sun axially withrespect to said sleeve shaft to maintain said balls in nonslippingfriction contact with said ring and suns comprising a Belleville washer,said washer having one portion thereof fixed to said sleeve shaft and asecond portion fixed to said second sun for preventing rotation of saidsun with respect to said sleeve shaft, a power delivery shaft extendingthrough said sleeve shaft, and means connecting said power deliveryshaft to said ring, said balls providing a support for rotatablysupporting said power delivery shaft in said sleeve shaft.

3. Power transmitting mechanism comprising a housing fixed againstrotation, a hollow sleeve support shaft fixed to said housing, a powerinput planet carrier, bearing means between said carrier and supportshaft supporting said carrier for rotation with respect to said supportshaft, a first sun supported on said support shaft and fixed againstrotation with respect to said shaft, a second sun supported upon saidsupport shaft and axially movable with respect thereto, a ring spacedfrom said suns, an extension on said carrier disposed in the spacebetween said ring and suns, a series of spaced pockets formed on saidextension, a ball roller disposed in each of said pockets and contactingsaid ring and said suns, an axially extending ear on said second sun, anotch on said support shaft, means for biasing said second sun axiallytoward said first sun to maintain said balls in nonslipping frictioncontact with said ring and said suns comprising a Belleville springwasher, a notch in said Belleville washer for receiving said ear, a tangon said washer extending into said support shaft notch, a power deliveryshaft, and means connecting said power delivery shaft to said ring forrotation therewith, said balls providing a support for rotatablysupporting said power delivery shaft in said support shaft.

4. An accessory drive for driving the accessories of an engine drivenvehicle comprising a support housing, a support sleeve fixed to saidhousing, an engine driven planet carrier, a planet roller driven by saidcarrier, a reaction sun supported on said support sleeve, 3. bearingbetween said carrier and support sleeve, a ring, said planet rollerbeing in friction contact with said sun and ring, a final power deliveryshaft connected to drive an engine accessory and having one endextending into said support sleeve, and means for supporting said oneend of said final power delivery shaft and for driving said powerdelivery shaft comprising a connection between said ring and powerdelivery shaft, said planet roller being effective to drive said ringand to support said ring and connection to thereby support said one endof said power delivery shaft.

5. In a power transmitting mechanism, a housing reaction member, a powerinput member, a power output member, plmli'l carrier means rotatablymounted in said housing member and connccred to one of said numbers fortransmitting torque, a plurality of equally spaced axial notches formedin said carrier having spaced parallel planar bearing surfaces facingeach other, a pair of opposirely disposed bearing inserts in each ofsaid notches and each bearing insert having a flat bearing surface inbearing contact with one of said planar bearing surfaces relativemovement and a concave substantially spherical surface formed on theside opposite said flat bearing surfaces to provide two facing sphericalsurfaces in each notch, a planet ball mounted between the facing concavespherical surfaces of each of said pairs of bearing inserts andextending beyond opposed sides of said carrier, the concave sphericalsurface of each of said inserts having a larger radius than the radiusof each of said planet balls providing a wedged opening between the balland each of said concave spherical surfaces whereby lubricant in saidwedged openings tends to lift said planet balls for full hydrodynamicspherical bearing lubrication, first ring means connected to another ofsaid members for transmitting torque and in friction-drive contact withsaid ball, second ring means connected to a third of said members fortransmitting torque and in friction-drive contact with said ball, andsaid first and second ring means axially and radially positioning saidball and including means to load said first and second ring means intororque-transmirting friction contact with said ball.

6. In a power transmitting mechanism, a housing reaction member, a powerinput member, a power output member, planet carrier means rotatablymounted in said housing member and connected to said power input memherfor transmitting torque, a plurality of equally spaced axial notchesformed in said carrier having spaced parallcl planar bearing surfacesfacing each olher, a pair of 0ppositely disposed bearing inserts in eachof said notches and each bearing insert having a flat bearing surface inbearing contact with one of said planar bearing surfaces and a concavesubstantially spherical surface formed on the side opposite said flatbearing surfaces to provide two facing spherical surfaces in each notch,a planet ball mounted between the facing concave spherical surfaces ofeach of said pairs of bearing inserts and extending beyond opposed sidesof said carrier, the concave spherical surface of each of said insertshaving a larger radius than the radius of each of said planet ballsproviding a wedged opening between the ball and each of said concavespherical surfaces whereby lubricant in said wedged openings tends tolift said planet balls for full hydrodynamic spherical bearinglubrication, a first ring means connected to said housing reactionmember for transmitting torque and in friction-drive contact with saidball, a second ring means connected to said power output member fortransmitting torque and in friction-drive contact with said ball, saidfirst and second ring means axially and radially positioning said balland including means to loud said first and second ring means intotorque-trons mining friction contact with said ball.

7. In a power transmitting mechanism, a housing reaction member, a powerinput member, a power output member, planet carrier means rotatablymounted in said housing member and connected to said power input memherfor transmitting torque, a plurality of equally spaced axial notchesformed in said carrier having spaced parallel planar bearing surfacesfacing each other, a pair of oppositely disposed bearing inserts in eachof said notches and each bearing insert having a flat bearing surface inbearing contact with one of said planar bearing surfaces and a concavesubstantially spherical surface formed on the side opposite said flatbearing surfaces to provide two facing spherical surfaces in each notch,a plant ball mounted between the facing concave spherical surfaces ofeach of said pairs of bearing inserts and extending beyond opposed sidesof said carrier, the concave spherical surface of each of said insertshaving a larger radius than the radius of each of said planet bullsproviding a wedged opening between the ball and each of said concavespherical surfaces whereby lubricant in said wedged openings tends tolift said planet balls for full hydrodynamic spherical bearinglubrication, split sun means connected to said housing reaction memberand in friction-drive contact with said ball, ring means connected tosaid power output member and in friction-drive contact with said ball,said sun and ring means axially and radially positioning said ball andmeans to load said split sun means into torque-transmitting frictioncontact with said ball and said ball into torque-transmitting frictioncontact with said ring means.

8. A power transmitting mechanism for driving the accessories of anengine-driven vehicle, said mechanism comprising a housing, a reactionmember secured to said housing, a power input 'member, a power outputmember, a planet carrier rotatably mounted in said housing and connectedto one of said members for transmitting torque, a plurality of equallyspaced radial passages having parallel side walls formed in saidcarrier, a sun member connected to a second of said members, a ringmember mounted radially outwardly of said parallel side walls andconnected to a third of said members, a pair of oppositely disposedbearing inserts secured by confinement between said parallel side wallsof each radial passage, a concave spherical surface formed on each ofsaid bearing inserts, a planet ball mounted between the concavespherical surfaces of each of said pairs of bearing inserts and infrictional contact with said sun and ring members, the concave sphericalsurface of each of said inserts having a larger radius than the radiusof each of said planet balls providing a wedged opening between the balland each of said concave spherical surfaces whereby lubricant in saidwedged openings tends to lift said planet balls for full hydrodynamicspherical bearing lubrication.

9. A power transmitting mechanism comprising a housing, a reactionmember secured to said housing, sun 'means axially slidably mounted onsaid reaction member, a power input member, a planet carrier rotatablymounted on said reaction member and driven by said input member, aplurality of equally spaced axial notches formed in said carrier, anoutput ring mounted radially outwardly of said notches, a pair ofoppositely disposed bearing inserts secured by confinement within eachof said notches, a concave spherical surface formed on each of saidbearing inserts, a planet ball mounted between the concave sphericalsurfaces of each of said pairs of bearing inserts and contacting saidsun means and said output ring, the concave spherical surface of each ofsaid inserts having a larger radius than the radius of each of saidplanet balls providing a wedged opening between the ball and each ofsaid concave spherical surfaces whereby lubricant in said wedgedopenings tends to lift said planet balls for full hydrodynamic sphericalbearing lubrication.

10. A power transmitting mechanism comprising a housing, a reactionmember secured to said housing, a sun member mounted on said reactionmember, a power input member, bearing means mounted on said reaction member, a planet carrier rotatably mounted on said bearing means and drivenby said input member, a power output member, a plurality of equallyspaced axial notches formed in said carrier, a ring member mountedradially outwardly of said notches, said power output member beingoperatively connected to said ring member, a pair of oppositely disposedbearing inserts secured by confinement within each of said notches, aconcave spherical surface formed on each of said bearing inserts, aplanet ball mounted between the concave spherical surfaces of each ofsaid pairs of bearing inserts, the concave spherical surface of each ofsaid inserts having a larger radius than the radius of each of saidplanet balls providing a wedged opening between the ball and each ofsaid concave spherical surfaces whereby lubricant in said wedgedopenings tends to lift said planet balls for full hydrodynamic sphericalbearing lubrication.

References Cited The following references, cited by the Examiner, are ofrecord in the patented file of this patent or the original patent.

UNITED STATES PATENTS 1,399,442 12/1921 Rennerfelt 74-798 1,574,8033/1926 Erban 74-798 1,585,140 5/1926 Erban 74208 X 1,691,625 11/1928Chilton 74-796 1,859,502 5/1932 Erban 74-208 X 1,915,287 6/1933 Bott308-187 2,953,039 9/1960 McRae 74-798 X 2,977,161 3/1961 Cobb 308-1873,021,730 2/1962 Banker 74-798 3,204,476 9/1965 Rouverol 74-1982,828,907 4/1958 Oehrli 74-796 2,874,592 2/1959 Oehrli 74-796 2,905,0269/ 1959 Oehrli 74796 2,913,932 11/1959 Oehrli 74-796 FOREIGN PATENTS313,969 6/1930 Great Britain.

MARK NEWMAN, Primary Examiner 'I'. C. PERRY, Assistant Examiner US. Cl.X.R.

mg UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No- RE..978 Dated November 17, 1970 InvenrorL's) Lubomyr O. Hewko It iscertified that error appears in the above-identified patent and thatsaid Letters Patent are hereby corrected as shown below:

Column 3, line 54,

"or" should read "on" Column 8, line 8,

"relative movement" should be deleted.

Signed and sealed this 21 at day of December 1 971 (SEAL) Attest:

EDWARD M.FLETCHER,JR. ROBERT GOTISCHALK Attesting Officer ActingCommissioner of Patents

